Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
CA 02833449 2013-11-15
DOMESTIC HOT WATER DELIVERY SYSTEM
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of United States Provisional
Application No. 61/727,186, filed
November 16, 2012.
FIELD OF THE INVENTION
[0002] The invention relates to the field of domestic hot water supply.
BACKGROUND
[0003] Most high rise residential buildings are provided with distribution
systems for two fluids:
= cold water
= tempered fluids
[0004] The tempered fluids are used by in-suite handling units for space
heating and cooling. The
most popular tempered fluid systems are: hybrid heat pump; water source heat
pump; two pipe fan coil;
and four pipe fan coil.
[0005] Domestic hot water is typically provided via one of:
= Centralized hot water
= in-suite electric tanks
= in-suite gas-fired tanks
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CA 02833449 2013-11-15
[0006] Each of the domestic hot water solutions has advantages and
disadvantages. The centralized
hot water system is relatively efficient, but requires additional piping
throughout the building and
requires individual flow meters, if cost is not to be shared uniformly. In-
suite electric hot water tanks
avoid the need for additional piping and metering, as the electricity would
normally be drawn from the
suite service that is typically monitored, but electric heating of water is
relatively expensive. In-suite
gas-fired water tanks provide relatively inexpensive hot water, but require
gas piping and venting
throughout the building, as well as flow meters, all of which would normally
not otherwise be required.
SUMMARY OF THE INVENTION
[0007] Forming one aspect of the invention is a system for providing domestic
water, heated domestic
water and space heating and cooling to a plurality of spaces.
[0008] This system comprises a domestic water distribution subsystem for
providing domestic water to
said plurality of spaces, a tempered fluid distribution subsystem for
tempering a fluid and providing
same to said plurality of spaces, air handling units adapted to transfer heat
between the fluid and the
plurality of spaces to provide for said space heating and cooling and a
plurality of arrangements for
providing heated domestic water.
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[0009] Each arrangement includes:
o a preheat tank coupled to the domestic water distribution subsystem for
receiving domestic water
therefrom;
o a heat exchanger coupled to the preheat tank in heat exchanging relation;
o a condenser, an evaporator, a refrigerant circuit including refrigerant,
a compressor and an
expansion valve, all coupled together to define a vapour compression
refrigeration arrangement
wherein heat is accepted in the evaporator in use and rejected in the
condenser in use;
o a control mechanism coupled to the tempered fluid distribution subsystem,
the heat exchanger and
the refrigeration arrangement and having: (i) a first operating mode, wherein
the fluid is routed
through the heat exchanger, to pass heat to the contents of the preheat tank;
and (ii) a second
operating mode, wherein the fluid is routed through the evaporator and the
refrigeration
arrangement is active, to pass heat to the refrigerant; and
o a water storage tank coupled to the preheat tank to receive water
therefrom and coupled to the
condenser in heat exchanging relation such that heat rejected by the condenser
is passed to the
contents of the hot water storage tank.
[0010] According to another aspect of the invention, in this system, the
control mechanism can have a
third operating mode, wherein heat is passed neither to the heat exchanger nor
the evaporator.
[0011] According to another aspect of the invention, in this system, the
tempered fluid distribution
subsystem can have a supply and a return and be selected from hybrid heat pump
system, water source
heat pump system and two pipe fan coil system; and the control mechanism can
have a fourth operating
mode, wherein the refrigeration arrangement is active and the fluid is routed
through the heat
exchanger and then through the evaporator to pass heat to the contents of the
preheat tank and then
to the refrigerant.
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[0012] According to another aspect of the invention, in this system, in use:
o the fluid can flow through the heat exchanger when: the temperature of
the fluid upstream of the
heat exchanger is materially higher than the temperature of the preheat tank
and the temperature
of the preheat tank is materially below the hot water tank set point
temperature;
o the fluid can not flow through the heat exchanger when the temperature of
the fluid upstream of
the heat exchanger is below the temperature of the preheat tank;
o the refrigeration arrangement can be inactive when the temperature of the
fluid upstream of the
evaporator is below the minimum safe operating temperature of the tempered
fluid subsystem;
o the refrigeration arrangement can be inactive when the temperature of the
hot water tank is
materially above the hot water set point temperature; and
o the refrigeration arrangement can be active when: the temperature of the
hot water tank is
materially below the set point temperature of the hot water tank; the
temperature of the fluid
upstream and downstream of the evaporator is materially above the minimum safe
operating
temperature of the tempered fluid subsystem; the temperature of the hot water
tank is falling; and
the temperature of the preheat tank is falling.
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[0013] According to another aspect of the invention, in this system:
o the refrigeration arrangement can be inactive when the temperature of the
preheat tank is
increasing and the temperature of the fluid downstream of the heat exchanger
is materially above
the set point temperature of the hot water tank; and
o the refrigeration arrangement can be active when the temperature of the
hot water tank is
materially below the set point temperature of the hot water tank, the
temperature of the fluid
upstream and downstream of the evaporator is materially above the minimum safe
operating
temperature of the tempered fluid subsystem, the temperature of the preheat
tank is stable and the
temperature in the hot water tank is falling.
[0014] According to another aspect of the invention, in this system, the
tempered fluid system can be
a hybrid heat pump system and the fluid can be provided in use to each of the
plurality of spaces at a
temperature which ranges from 75F in summer to 130F in winter.
[0015] According to another aspect of the invention, in this system, the fluid
can be provided in use to
each of the plurality of spaces at a temperature which ranges from about 85F
in summer to about 120F
in winter.
[0016] According to another aspect of the invention, in this system, the
tempered fluid system can be
a water source heat pump and the fluid can be provided in use to each of the
plurality of spaces at a
temperature that ranges between 105F in summer and 55F in winter, or, more
specifically, at a
temperature that ranges between about 90F in summer and about 60F in winter.
[0017] According to another aspect of the invention, in this system, the
tempered fluid subsystem can
be a two pipe fan coil system; in summer, the fluid can be provided in use to
each of the plurality of
spaces at a temperature between 40F and 60F; and in winter, the fluid can be
provided in use to each of
the plurality of spaces at a temperature between 100F and 180F.
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[0018] According to another aspect of the invention, in this system: in
summer, the fluid can be
provided in use to each of the plurality of spaces at a temperature of about
45F; and in winter, the fluid
can be provided in use to each of the plurality of spaces at a temperature of
about 130F.
[0019] According to another aspect of the invention, in this system:
= the control mechanism can be defined by: a fluid circuit coupling the
tempered water subsystem
supply to the tempered water subsystem return and in which the evaporator is
interposed; a control
valve interposed in the fluid circuit upstream of the evaporator; a three way
valve interposed in the
fluid circuit upstream of the control valve; and a shunt fluid circuit
providing a parallel path from the
tempered water subsystem supply to the three way valve and in which the heat
exchanger is
interposed
= the first operating mode can be defined by a position of the 3-way valve
that provides for flow
through the heat exchanger, a position of the control valve that provides for
flow through the
evaporator and an inactive vapour compression refrigeration arrangement;
= the second operating mode can be defined by a position of the 3-way valve
that provides for flow
which bypasses the heat exchanger, a position of the control valve that
provides for flow through
the evaporator and an active vapour compression refrigeration arrangement;
= the third operating mode can be defined by a position of the control
valve that arrests flow and an
inactive vapour compression refrigeration arrangement; and
= the fourth operating mode can be defined by a position of the 3-way valve
that provides for flow
through the heat exchanger, a position of the control valve that provides for
flow through the
evaporator and an active vapour compression refrigeration arrangement.
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[0020] According to another aspect of the invention, in this system:
= the tempered fluid subsystem can be a four pipe fan coil system including
a chilled water supply,
a hot water supply, a chilled water return and a hot water return;
= the tempered fluid distribution system can provide to each of the
plurality of spaces: (i) hot
water, at a temperature that ranges from 160F in winter to 80F in summer; and
(ii) at least in
summer, chilled water, at a temperature in the range of 40-60F; and
= the control mechanism can be coupled to the tempered fluid distribution
subsystem, the heat
exchanger and the refrigeration arrangement such that, in the first operating
mode, the hot
water is routed through the heat exchanger, to pass heat to the contents of
the preheat tank;
and in the second operating mode, the chilled fluid is routed through the
evaporator and the
refrigeration arrangement is active, to pass heat to the refrigerant.
[0021] According to another aspect of the invention, in this system, the
tempered fluid distribution
system can provide to each of the plurality of spaces: (i) hot water, at a
temperature that ranges from
130F in winter to 120F in summer; and (ii) at least in summer, chilled water,
at a temperature of about
45F.
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[0022] According to another aspect of the invention, in this system,
o the hot water can flow through the heat exchanger when the temperature of
the hot water
upstream of the heat exchanger is materially higher than the temperature of
the preheat tank and
the temperature of the preheat tank is materially below the hot water tank set
point temperature;
o the hot water can not flow through the heat exchanger when the
temperature of the hot water
upstream of the heat exchanger is below the temperature of the preheat tank;
o the refrigeration arrangement can be inactive when the temperature of the
hot water tank is
materially above the hot water set point temperature;
o the refrigeration arrangement can be active when the temperature of the
hot water tank is
materially below the set point temperature of the hot water tank, the
temperature of the hot water
tank is falling and the temperature of the preheat tank is falling;
o the refrigeration arrangement can be inactive when the temperature of the
preheat tank is
increasing and the temperature of the hot water downstream of the heat
exchanger is materially
above the set point temperature of the hot water tank; and
o the refrigeration arrangement can be active when the temperature of the
hot water tank is
materially below the set point temperature of the hot water tank, the
temperature of the preheat
tank is stable and the temperature in the hot water tank is falling.
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[0023] According to another aspect of the invention, in this system:
= the control mechanism is defined by: (i) a first fluid circuit in which
the heat exchanger is interposed
which couples the hot water supply to the hot water return; (ii) a second
fluid circuit in which the
evaporator is interposed which couples the chilled water supply to the chilled
water return; (iii) a
first control valve interposed in the first fluid circuit; and (iv) a second
control valve interposed in
the second fluid circuit;
= the first operating mode is defined by a position of the first control
valve that provides for flow
through the heat exchanger, a position of the second control valve that arrest
flow through the
evaporator and an inactive vapor compression refrigeration arrangement;
= the second operating mode is defined by a position of the first control
valve that arrests flow
through the heat exchanger, a position of the second control valve that
provides for flow through
the evaporator and an active vapor compression refrigeration arrangement; and
= the third operating mode is defined by a position of the first control
valve that arrests flow through
the heat exchanger, a position of the second control valve that arrest flow
through the evaporator
and an inactive vapor compression refrigeration arrangement.
[0024] Forming yet another aspect of the invention is a water heater
arrangement for use with a
domestic water distribution subsystem and a tempered fluid distribution
subsystem. The tempered
fluid distribution subsystem is of the type adapted to temper a fluid and
provide same to a plurality of
spaces, having a supply and a return and being selected from hybrid heat pump
system, water source
heat pump system and two pipe fan coil system.
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[0025] This arrangement comprises:
o a preheat tank coupled to the domestic water distribution subsystem for
receiving water therefrom;
o a heat exchanger coupled to the preheat tank in heat exchanging relation;
o a condenser, an evaporator, a refrigerant circuit including refrigerant,
a compressor and an
expansion valve, all coupled together to define a vapour compression
refrigeration arrangement
wherein heat is accepted in the evaporator in use and rejected in the
condenser in use;
o a control mechanism coupled to the tempered fluid distribution subsystem,
the heat exchanger and
the refrigeration arrangement and having: (i) a first operating mode, wherein
the fluid is routed
through the heat exchanger, to pass heat to the contents of the preheat tank;
(ii) a second
operating mode, wherein the fluid is routed through the evaporator and the
refrigeration
arrangement is active, to pass heat to the refrigerant; (iii) a third
operating mode, wherein heat
from the fluid is passed neither through the heat exchanger nor the
evaporator; and (iv) a fourth
operating mode, wherein the fluid is routed through the heat exchanger and
then through the
evaporator to pass heat to the contents of the preheat tank and then to the
refrigerant; and
o a water storage tank coupled to the preheat tank to receive water
therefrom and coupled to the
condenser in heat exchanging relation such that heat rejected by the condenser
is passed to the
contents of the hot water storage tank.
CA 02833449 2013-11-15
[0026] According to another aspect of the invention, in this arrangement:
= the control mechanism can be defined by: (i) a fluid circuit coupling the
tempered water subsystem
supply to the tempered water subsystem return and in which the evaporator is
interposed; (ii) a
control valve interposed in the fluid circuit upstream of the evaporator;
(iii) a three way valve
interposed in the fluid circuit upstream of the control valve; and (iv) a
shunt fluid circuit providing a
parallel path from the tempered water subsystem supply to the three way valve
and in which the
heat exchanger is interposed; and
= the first operating mode can be defined by a position of the 3-way valve
that provides for flow
through the heat exchanger, a position of the control valve that provides for
flow through the
evaporator and an inactive vapor compression refrigeration arrangement;
= the second operating mode can be defined by a position of the 3-way valve
that provides for flow
which bypasses the heat exchanger, a position of the control valve that
provides for flow through
the evaporator and an active vapor compression refrigeration arrangement;
= the third operating mode can be defined by a position of the control
valve that arrests flow and an
inactive vapor compression refrigeration arrangement; and
= the fourth operating mode can be defined by a position of the 3-way valve
that provides for flow
through the heat exchanger, a position of the control valve that provides for
flow through the
evaporator and an active vapor compression refrigeration arrangement.
[0027] A water heater arrangement for use with a domestic water distribution
subsystem and with a
tempered fluid distribution subsystem forms another aspect of the invention.
This tempered fluid
subsystem is a four pipe fan coil system including a chilled water supply, a
hot water supply, a chilled
water return and a hot water return.
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[0028] This arrangement cornprises:
o a preheat tank coupled to the domestic water distribution subsystem for
receiving water therefrom;
o a heat exchanger coupled to the preheat tank in heat exchanging relation;
o a condenser, an evaporator, a refrigerant circuit including refrigerant,
a compressor and an
expansion valve, all coupled together to define a vapour compression
refrigeration arrangement
wherein heat is accepted in the evaporator and rejected in the condenser;
o a control mechanism coupled to the tempered fluid distribution subsystem,
the heat exchanger and
the refrigeration arrangement and having: (i) a first operating mode, wherein
the hot water supply is
routed through the heat exchanger, to pass heat to the contents of the preheat
tank; and (ii) a
second operating mode, wherein the chilled water supply is routed through the
evaporator and the
refrigeration arrangement is active, to pass heat to the refrigerant; and
o a water storage tank coupled to the preheat tank to receive water
therefrom and coupled to the
condenser in heat exchanging relation such that heat rejected by the condenser
is passed to the
contents of the hot water storage tank.
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[0029] According to another aspect of the invention, in this arrangement:
o the control mechanism can also have a third operating mode, wherein the
hot water supply
bypasses the heat exchanger and the chilled water supply bypasses the
evaporator; and
o the control mechanism can be defined by: a first fluid circuit in which
the heat exchanger is
interposed which couples the hot water supply to the hot water return; a
second fluid circuit in
which the evaporator is interposed which couples the chilled water supply to
the chilled water
return; a first control valve interposed in the first fluid circuit; and a
second control valve interposed
in the second fluid circuit,
and:
o the first operating mode can be defined by a position of the first
control valve that provides for flow
through the heat exchanger, a position of the second control valve that arrest
flow through the
evaporator and an inactive vapor compression refrigeration arrangement;
o the second operating mode can be defined by a position of the first
control valve that arrests flow
through the heat exchanger, a position of the second control valve that
provides for flow through
the evaporator and an active vapor compression refrigeration arrangement; and
o the third operating mode can be defined by a position of the first
control valve that arrests flow
through the heat exchanger, a position of the second control valve that arrest
flow through the
evaporator and an inactive vapor compression refrigeration arrangement.
[0030] Other advantages, features and benefits of the present invention, will
become apparent upon a
review of the following detailed description and drawings, the latter being
briefly described hereinafter.
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BRIEF DESCRIPTION OF THE DRAWINGS
[0031] FIG. 1 is a schematic view of the main components of an arrangement for
providing heated
domestic water according to an exemplary embodiment of the invention;
[0032] FIG. 2 shows a schematic view of an arrangement according to an
exemplary embodiment of
the invention coupled for use with a two pipe tempered fluid system of the
type used
for space heating;
[0033] FIG. 3 is a view similar to FIG. 2, showing a first operating mode;
[0034] FIG. 4 is a view similar to FIG.2, showing a second operating mode;
[0035] FIG. 5 is a view similar to FIG. 3, showing a third operating mode;
[0036] FIG. 6 shows a schematic view of an arrangement according to an
exemplary embodiment of
the invention in use with a four pipe fan coil HVAC system.
DETAILED DESCRIPTION
[0037] FIG. 1 shows, in schematic form, the main components of an arrangement
20 for providing
heated domestic water according to an exemplary embodiment of the present
invention.
[0038] Herein, it will be seen that the main components of the arrangement 20
include: a preheat tank
22, a heat exchanger 24, a condenser 26, an evaporator 28, a refrigerant
circuit 30 including refrigerant,
a compressor 32, an expansion valve 34 and a water storage tank 36.
[0039] The preheat tank 22 has an inlet 38 and an outlet 40.
[0040] The heat exchanger 24 is coupled to the preheat tank 22 in heat
exchanging relation and is
defined by a coil disposed interiorly of the preheat tank 22.
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[0041] Condenser 26, evaporator 28, refrigerant circuit 30 including
refrigerant, compressor 32 and
expansion valve 34 are all coupled together to define a vapour compression
refrigeration arrangement
42 wherein heat is accepted in the evaporator 28 and rejected in the condenser
26. The condenser 26
will be seen in this embodiment to be a coil.
[0042] The water storage tank 36
= is disposed in heat exchanging relation to, namely, interiorly of, the
condenser coil 26 such that
heat rejected by the condenser 26 is passed to the contents of the hot water
storage tank 36;
= has an inlet 44 coupled to the outlet 40 of the preheat tank; and
= has an outlet 46 from which heated water can be withdrawn in use.
[0043] In the structure shown, the water storage tank 36 and the preheat tank
22 are defined by
portions of larger tank, with the inlet 44 of the water storage tank 36 and
the outlet 40 of the preheat
tank being defined by an aperture in a sloping dividing wall. A further
aperture 43 is also defined in
the sloped divider and allows, inter alia, for relatively cooler water in the
water storage tank 36 to
displace relatively warmer water in the preheat tank 22, if the situation
arises.
[0044] As will become apparent upon further consideration, the arrangement is
advantageously used
as part of a system for providing domestic water, heated domestic water and
space heating and cooling
to a plurality of spaces, such as high-rise residential buildings, the system
being of the type including a
domestic water distribution subsystem for providing domestic water to said
plurality of spaces; a
tempered fluid distribution subsystem for providing tempered fluid to said
plurality of spaces; and air
handling units adapted to transfer heat between the tempered fluid and the
plurality of spaces to
provide for said space heating and cooling. When used as part of such a
system, an arrangement as
shown in elemental form in FIG.1 is provided for each space to be provided
with heated domestic water,
and substitutes for a conventional water heater, as described hereinafter.
CA 02833449 2013-11-15
[0045] An exemplary use of the arrangement is in the context of a high-rise
residential building having
a tempered fluid distribution subsystem including a single supply and a single
return. Tempered fluid
distribution subsystems of this type include hybrid heat pump systems, water
source heat pump
systems and two pipe fan coil system, and reference is now made to FIG. 2
which shows an arrangement
according to an exemplary embodiment of the invention and including the
elements of FIG. 1 as used in
a high-rise residential building having a tempered fluid system of this type.
[0046] Herein will be seen:
= the tempered water subsystem supply 50
= the tempered water subsystem return 52
= the preheat tank 22, heat exchanger 24, condenser 26, evaporator 28,
refrigerant circuit 30
including refrigerant, compressor 32, expansion valve 34 and water storage
tank 36, as
previously described, the inlet 38 of the preheat tank 22 now being coupled to
a domestic water
distribution subsystem 54 for receiving domestic water therefrom.
= a fluid circuit 56 coupling the tempered water subsystem supply 50 to the
tempered water
subsystem return 52 and in which the evaporator 28 is interposed; a control
valve 58 interposed
in the fluid circuit 56 upstream of the evaporator 28; a three way valve 60
interposed in the fluid
circuit 56 upstream of the control valve 60; and a shunt fluid circuit 62
providing a parallel path
from the tempered water subsystem supply 50 to the three way valve 60 and in
which the heat
exchanger 24 is interposed, all collectively defining a control mechanism that
has four operating
modes
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First Operating Mode - Passive Reclaim
[0047] The first operating mode is defined by a position of the 3-way valve 60
that provides for flow
through the heat exchanger 24, a position of the control valve 58 that
provides for flow through the
evaporator 28 and an inactive vapour compression refrigeration arrangement 42,
all as shown in FIG. 3.
In the first operating mode, the tempered fluid is routed through the heat
exchanger 24, to pass heat to
the contents of the preheat tank 22.
Second Operating Mode ¨ Active Reclaim
[0048] The second operating mode is defined by a position of the 3-way valve
60 that provides for flow
which bypasses the heat exchanger 24, a position of the control valve 58 that
provides for flow through
the evaporator 28 and an active vapour compression refrigeration arrangement
42, all as shown in FIG.
4. In the second operating mode, the tempered fluid is routed through the
evaporator 28 and the
refrigeration arrangement is active, such that heat is passed to the
refrigerant.
Third Operating Mode - Inactive
[0049] The third operating mode, as shown in FIG. 2, is defined by a position
of the control valve 58
that arrests flow and an inactive vapour compression refrigeration arrangement
42. In this mode, heat
is passed neither to the heat exchanger nor the evaporator.
Fourth Operating Mode ¨ Passive and Active Reclaim
[0050] The fourth operating mode is defined by a position of the 3-way valve
60 that provides for flow
through the heat exchanger 24, a position of the control valve 58 that
provides for flow through the
evaporator 28 and an active vapour compression refrigeration arrangement 42.
In the fourth operating
mode, as shown in FIG. 5, the tempered fluid is routed through the heat
exchanger 24 and then through
the evaporator to pass heat to the contents of the preheat tank 22 and then to
the refrigerant.
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Mode Selection
[0051] In the context of hybrid heat pump systems, water source heat pump
systems and two pipe fan
coil system, the controller is adapted to switch between modes in a generally
similar fashion:
o the fluid flows through the heat exchanger when: the temperature of the
fluid upstream of the heat
exchanger is materially higher than the temperature of the preheat tank and
the temperature of the
preheat tank is materially below the hot water tank set point temperature;
o the fluid does not flow through the heat exchanger when the temperature
of the fluid upstream of
the heat exchanger is below the temperature of the preheat tank;
o the refrigeration arrangement is inactive when the temperature of the
fluid upstream of the
evaporator is below the minimum safe operating temperature of the tempered
fluid subsystem;
o the refrigeration arrangement is inactive when the temperature of the hot
water tank is materially
above the hot water set point temperature;
o the refrigeration arrangement is active when: the temperature of the hot
water tank is materially
below the set point temperature of the hot water tank; the temperature of the
fluid upstream and
downstream of the evaporator is materially above the minimum safe operating
temperature of the
tempered fluid subsystem; the temperature of the hot water tank is falling;
and the temperature of
the preheat tank is falling.
o the refrigeration arrangement is inactive when the temperature of the
preheat tank is increasing
and the temperature of the fluid downstream of the heat exchanger is
materially above the set
point temperature of the hot water tank; and
o the refrigeration arrangement is active when the temperature of the hot
water tank is materially
below the set point temperature of the hot water tank, the temperature of the
fluid upstream and
downstream of the evaporator is materially above the minimum safe operating
temperature of the
tempered fluid subsystem, the temperature of the preheat tank is stable and
the temperature in the
hot water tank is falling.
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[0052] Numerous references are made above [and in subsequent passages] to
"material" temperature
differences. In this regard, it will be appreciated that, to avoid excessive
cycling, it will be necessary to
set, for example, "rise" and "drop" thermostatic differentials, i.e., when the
tempered fluid is warmer
than the preheat tank, the fluid will be passed through the heat exchanger
until the preheat tank is quite
a bit warmer than the desired set point, and then will not be cycled through
again until the temperature
in the preheat tank has fallen below the set point. Similarly, in the context
of a AT for heat exchange
purposes, it will be appreciated that when AT becomes relatively small, heat
exchange will slow down
significantly, to the point that the cost of pumping fluid through the heat
exchanger may well
overwhelm the amount of free heat obtained. Persons of ordinary skill will
readily understand (i) that
the concept of "material" differences as described herein addresses both the
problems of unnecessary
thermostatic cycling and diminishing heat exchange returns, and (ii) the
manner in which computer
controls can be implemented to achieve these goals. Accordingly, further
description of this concept
and the manner in which it is implemented to achieve the goals of the present
invention are neither
required nor disclosed.
[0053] The outcome of the mode selection depends upon the nature of the
tempered fluid distribution
system in use and the thermodynamic capacity of the hot water arrangement.
Hybrid Heat Pump System
[0054] In hybrid heat pump systems, the tempered fluid supply is available
year round with a
temperature [Ti in FIGS. 2-5] that ranges from about 75 in summer and 130F in
winter. In this
application, an operating regime that has significant advantage in climates
such as that in Southern
Ontario, Canada, is a tempered fluid supply that is about 85F in summer and
about 130F in winter. In
this operation, with a domestic hot water supply set for 120F and an
arrangement wherein the preheat
tank is about 20% of the volume of the hot water tank, the temperature of the
contents of the preheat
tank 22 [T2 in FIGS. 2-5] will be maintained at about 80F in summer and at
about 100F in winter.
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Water Source Heat Pump System
[0055] In water source heat pump systems, the tempered fluid supply is
available year round with a
temperature Ti that ranges between about 105F in summer and about 55F in
winter. In this
application, an operating regime that has significant advantage in climates
such as that in Southern
Ontario, Canada, is a tempered fluid supply that is set at about 90F in summer
and about 60F in winter.
In this operation, with a domestic hot water supply set for 120F and an
arrangement wherein the
preheat tank is 20% of the volume of the hot water tank, the temperature T2 of
the contents of the
preheat tank 22 will be maintained at about 80F in summer and at about 55F in
winter.
Two Pipe Fan Coil System
[0056] In two pipe fan coil systems, the temperature Ti of the tempered fluid
supply changes with the
season: in the summer, tempered fluid is made available at about 40F-60F, for
space cooling; in winter,
the tempered fluid is made available at between 100F and 180F, for space
heating. In this application,
an operating regime that has significant advantage in climates such as that in
Southern Ontario, Canada,
is a tempered fluid supply that is set at about 45F in summer and about 130F
in winter. In this
operation, with a domestic hot water supply set for 120F and an arrangement
wherein the preheat tank
is 20% of the volume of the hot water tank, the temperature T2 of the preheat
tank 22 will be
maintained at about 120F in winter; the preheat tank 22 will be bypassed in
summer entirely; and the
refrigeration unit will be inactive in winter.
CA 02833449 2013-11-15
Four Pipe Fan Coil Systems
[0057] The arrangement can also be utilized in the context of 4-pipe fan coil
systems including a chilled
water supply, a hot water supply, a chilled water return and a hot water
return. FIG. 6 shows an
arrangement according to an exemplary embodiment of the invention and
including the elements of
FIG. 1 as used in a high-rise residential building having a tempered fluid
system of this type; herein will
be seen:
= the hot water supply 70 and return 72 and the chilled water supply 74 and
return 76
= the preheat tank 22, heat exchanger 24, condenser 26, evaporator 28,
refrigerant circuit 30
including refrigerant, compressor 32, expansion valve 34 and water storage
tank 36, as
previously described, the preheat tank 22 being coupled to a domestic water
distribution
subsystem (not shown) for receiving domestic water therefrom
= a first fluid circuit 78 in which the heat exchanger is interposed which
couples the hot water
supply 70 to the hot water return 72; a second fluid circuit 79 in which the
evaporator 28 is
interposed which couples the chilled water supply 74 to the chilled water
return 76; a first
control valve 80 interposed in the first fluid circuit 78; and a second
control valve 82 interposed
in the second fluid circuit 79, collectively defining a control mechanism
having three operating
modes.
First Operating Mode ¨ Passive Reclaim
[0058] The first operating mode is defined by a position of the first control
valve 80 that provides for
flow through the heat exchanger, a position of the second control valve that
arrest flow through the
evaporator and an inactive vapor compression refrigeration arrangement. In the
first operating mode,
the tempered fluid is routed through the heat exchanger, to pass heat to the
contents of the preheat
tank.
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CA 02833449 2013-11-15
Second Operating Mode ¨ Active Reclaim
[0059] The second operating mode is defined by a position of the first control
valve that arrests flow
through the heat exchanger, a position of the second control valve that
provides for flow through the
evaporator and an active vapor compression refrigeration arrangement. In the
second operating mode,
the tempered fluid is routed through the evaporator and the refrigeration
arrangement is active, such
that heat is passed to the refrigerant.
Third Operating Mode
[0060] The third operating mode is defined by a position of the first control
valve that arrests flow
through the heat exchanger, a position of the second control valve that arrest
flow through the
evaporator and an inactive vapor compression refrigeration arrangement. In
this mode, heat is passed
neither to the heat exchanger nor the evaporator.
Use
[0061] In four pipe fan coil systems, two supplies of tempered fluid are
typically available: a hot fluid,
which ranges between 160F in winter and 80F in summer, and a chilled fluid,
which ranges between 40F
and 60F. In winter conditions, the chilled fluid circuit may be disabled.
[0062] In this application, an operating regime that has significant advantage
in climates such as that in
Southern Ontario, Canada, is a hot water supply maintained at about 130F in
winter and a chilled
water supply maintained at about 45F in summer.
[0063] In this operation, with a domestic hot water supply set for 120F and an
arrangement wherein
the preheat tank is 20% of the volume of the hot water tank, the preheat tank
22 will be maintained at
about 120F in winter; the preheat tank 22 will be bypassed in summer entirely;
and the refrigeration
unit will be inactive in winter.
22
CA 02833449 2013-11-15
Benefits and Advantages
[0064] In many structures, there is excess available heat in the building
systems that can be used to
provide some or most of the heat required for warming domestic hot water
passively.
[0065] If there is excess heat available in the building systems, but the
temperature is too low to
permit passive heat exchange to the domestic water tank, the heat can be
extracted by the refrigeration
arrangement at a COP of about 4. Importantly, this COP only applies to the
water heated in the storage
tank. For example, with a hybrid system with 90F fluids, the overall COP would
be about 8, with 50F
entering DW and 120F supply DW temperature.
[0066] During periods when the building systems do not have an excess of heat
and are being
supplemented by high efficiency condensing boilers the bulk of the heat will
come from natural gas with
efficiencies far exceeding that of normal gas fired hot water heaters.
[0067] On buildings that would normally incorporate in-suite gas fired hot
water tanks will eliminate
the need for a gas distribution system and flue venting. This approach can
save significant energy and
cost [operating and capital]
[0068] On buildings that would normally have electric hot water tanks, the
invention can save
significant energy and costs.
Effectiveness Operating Examples
[0069] Prophetic examples are described below to further demonstrate the
performance of the
apparatus. The examples relate to the apparatus as applied in a hybrid heat
pump system in a typical
condominium installation. It will be understood that this is a representative
application, only.
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CA 02833449 2013-11-15
[0070] By way of background, the following assumptions are made:
a) The average consumption of domestic hot water in a high rise
apartment/condominium is 40 US
gallons per day. This information comes from the ASHRAE Applications Handbook.
b) Domestic cold water temperatures supplied through the ground piping
systems average 50 F in
the Northern US and Southern Canada. Tank temperatures are normally maintained
at 130 F.
c) Heat required to provide 40 gallons of 130 F water per day is
40x8.33x(130 -50 )=26,600 BTU's.
Tank heat loss is approximately 6,000 BTU for a total heat load of 32,000
BTU's/day
d) Each and every building and each and every suite in a high rise
residential is different, varying by
location, occupancy, and construction. In the examples, in order to evaluate
and provide a
comparison of domestic water heating systems, the year has been broken down
into 4 periods.
These are summer [June, July & August in North America] where at all times the
building will be
rejecting heat through the HVAC system; winter [December, January & February]
when there is
no excess heat available from the HVAC system; and spring and fall, wherein it
is assumed for
the purpose of the examples that 50% of the heat will be available from the
HVAC system.
e) While energy rates vary significantly by location, and in some cases by
time of day, for simplicity,
the examples reflect a rate of 5.12/kwh for electricity and $1.20/therm for
natural gas at 100%
efficiency.
[0071] Domestic water heating systems commonly in use for this type of
building are as follows:
1) Individual Electric Water Heating Tanks
2) Individual Gas Fired Water Heating Tanks
3) Central Gas Fired System
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CA 02833449 2013-11-15
[0072] The following is the energy and cost calculations for each of these
methods of domestic water
heating.
Individual Electric Water Heating Tanks
Installation Tank Costs ¨ Low Electrical
Wiring Costs¨ High
Calculations 32,000 BTU/day = 9.4 kW/day
Electric Heating = 100% Efficiency
9.4 kW/day = 3,420 kW/year
At $.12/kW = $410/year
Energy Consumed 3,420 kW/yr
Recycled 0 kW
Individual Gas Fired Water Heating Tanks
Installation- Tank Cost ¨ Low Gas Piping Costs
¨ Very High
Calculations Gas Heaters are 80% Efficient
Gas Consumer/day 32,000/.8/10000 = .4 Therms/day
Annual Gas Consumption/year = .4 x 365 = 146 therms
Annual Gas Costs/Suite = 146x$1.20 = $175.20/year
Energy Consumed 146 therms = 4278 kW
Recycled 0 kW
Centralized Domestic Hot Water Heating System ( per suite basis)
Installation Boilers/ Storage Tanks ¨ Expensive
Hot Water Piping Through Building ¨ Expensive
Calculations Gas Boilers are 80% Efficient
Line Heat Losses 33%
Gas Consumer/day 26,600/.8/(1-.33)/10000 = 485 Therms/day
Annual Gas Consumption/year = 485 x 365 = 177 the
Annual Gas Costs/Suite = 177x$1.20 = $212.20/year
Energy Consumed - 177 therms = 5186 kW
Recycled 0 kW
CA 02833449 2013-11-15
Exemplary inventive Hybrid Heat Pump System
[0073] The following is the energy and cost calculation for the mentioned
typical condominium
installation of the exemplary apparatus and using the same assumptions as
indicated above.
Installation - Tank Cost ¨ Expensive
Piping Costs ¨ Low
Electrical Costs ¨ Medium
Calculations - Season Summer Winter Spring/Fall
Days 121 121 243
System Fluid Temperature 90 F 100 F 85 F
PreHeat Tank Effectiveness 80% 80% 80%
Water Temp Rise 80%x(90*-501=
32 F 40 F 28
Passive Heating 32770 02,000=
14,600 BTU 18,300 12,800
Source Recycled 100% Gas 50% Gas
Non Passive Heating 32,000-14,600=
17,400 BTU 13,700 19,200
Source Recycled 75% 0% 37%
Gas 0% 75% 37%
Electric 25% 25% 25%
Gas Used/Yr (18,300x100%+13,700x75%)x121/100,000/95% @95% Boiler Eff
0 =36.4 therm 34.6 therms
Electrical 17,400x.25/3413x121=
154 kW 121 kW 342 kW
Total Gas 71 therms @ $1.20 = $85.20/Year
Total Electric 617 kW @ $.12/kWh= $74.00/Year
Total Cost $159.24/yr
Energy Consumed 2697 kWh
Energy Recovered 732 kWh
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Comparisons
[0074] These comparisons show the annual operating cost savings and annual
energy savings in both
dollars and percentages provided by the Domestic Water Heat Recovery Unit
[inventive hybrid heat
pump] over other conventional systems
DWHRU Electric Tank Gas Tank Gas Central
Annual Costs $159.24 $410.00 $175.20 $212.20
Savings/yr $0 $250.76 $15.96 $52.96
% Annual Cost Savings 61% 9% 25%
Energy Usage 2697kWh/yr 3420kWh/hr 4278kWh/yr 5186kWh/yr
Energy savings 732kWh/yr 1581kWh/yr 2489kWh/yr
% Energy Savings 21% 37% 48%
Variations and modifications
[0075] Whereas various operating conditions and thermodynamic capacities are
herein described in
detail, it will be evident that modifications can be made, including but not
limited to:
o the volume of the preheat tank can vary and need not represent 20% of the
volume of the hot
water tank
o the recovery rate of the heat exchanger can vary
o the hot water tank set point need not be set at 120F as indicated
o the material difference embodied in the controller for the purpose of
oscillation avoidance can,
for example only, be 2F
o the material difference embodied in the controller for the purpose of
prolonged cycling can, for
example only, be 5F
o the control mechanism can be embodied with other arrangements of valves
and fluid circuits
o the operating conditions of the tempered fluid subsystem can be other
than those specified
[0076] Accordingly, the invention should be understood as limited only by the
accompanying claims,
purposively construed.
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